KR20110021713A - Transmission device for a machine for porducing electricity from a variable-speed motive source, unit for producing electricity and wind machine both so equipped, and method of adjusting a transmission ratio - Google Patents

Abstract

The same two differential mechanisms 13, 113 are connected between the input shaft 11 connected to the rotor 1 of the wind generator by the speed increasing device 4 and the output shaft 12 connected to the synchronous generator 3. Is mounted. Two planetary gears 14, 114 are engaged to the output shaft 12. Two planet carriers 17, 117 are bound to the input shaft 11. Thus, the two annulus gears 16, 116 rotate at the same speed. They are connected to the two input elements 22, 23 of the comparison differential mechanism 141 via slightly different speed ratios 66, 166 reversing with respect to each other. The cage 146 of the differential mechanism 141 rotates at half the speed of the absolute difference between the rotational speeds of the elements 22, 23. After multiplication by the gear parts 147, 148, this low speed is applied to the rotor 133 of the regulating device 32, such as an electric generator. The speed ratio is adjusted or regulated by adjusting the torque applied by the regulating generator 32. By completely stabilizing the rotational speed of the synchronous generator 3 and allowing it to be constantly connected to the network using the regulating device 32, only a small amount of energy is consumed.

Description

TRANSMISSION DEVICE FOR A MACHINE FOR PORDUCING ELECTRICITY FROM A VARIABLE-SPEED MOTIVE SOURCE, UNIT FOR PRODUCING ELECTRICITY AND WIND MACHINE BOTH SO EQUIPPED, AND METHOD OF ADJUSTING A TRANSMISSION RATIO}

FIELD OF THE INVENTION The present invention relates to the field of wind turbines or to other fields related to generators connected to variable-speed motive power sources.

More specifically, the invention relates to a transmission of a machine that produces power from a variable speed power source, in particular a wind turbine rotor.

The invention also relates to a unit which is driven by a wind turbine rotor to produce power.

Furthermore, the present invention relates to a wind turbine equipped with a transmission or a unit for producing electric power.

At present, the use of wind turbines is quite limited because of the still high production or running costs compared to efficiency. Therefore, lowering the cost per kilowatt produced by wind turbines is key. This is also a necessary prerequisite for high power wind turbine booms capable of producing high capacity power such as several megawatts.

One of the main difficulties is that the wind turbine rotor must produce a stable frequency current even though the speed of rotation of the wind turbine's rotation is in a fairly wide range, which is also related to the variation in wind speed in a fairly wide range. It is. In general, efforts are underway to operate wind turbines between a minimum speed at which wind speeds are close to zero and a maximum speed at 15 m / s. The rotational speed of the wind turbine rotor generally varies between one and thirty revolutions per minute.

There are various proposals to solve this problem. First of all, most of the installed wind turbines are asynchronous generators, which allows a small range of speed changes in the generator input shaft. To improve the suitability of extending the range of speeds, some manufacturers connect their wind turbines with two generators, the small ones used during low winds and the larger ones used during high winds.

Also known are wind turbines having generators in which the number of poles is variable. By varying the number of connected electrodes, such generators can operate even with different numbers of electrodes, thus responding to varying rotational speeds.

In all cases, the frequency of the produced current changes as a function of the rotational speed of the generator, making it impossible to connect to the grid or requiring a complicated conversion process to obtain a frequency suitable for the grid. In particular, the two-generator technique involves switching from one generator to another on supply to the grid, thus adjusting the frequency and phase of the generated current with those in the grid. There is a need. These problems increase installation costs and do not significantly improve the efficiency of wind turbines.

In addition, a transmission for a wind turbine generator has been known through international publication WO 2004 / 088132A1. The device utilizes a main route of transmission between the wind turbine rotor and the rotor of the generator and a parrellel regulating route with a hydraulic torque converter. However, it is not enough to stabilize the generator drive speed. The frequency of the produced current will fluctuate between 50 and 60 hertz. The converter wastes energy as heat.

International publication WO 81/01444 provides a parallel adjustment path between a rotor and a generator shaft through a hydraulic, mechanical or electronic variableator. The transmission is controlled according to two signal functions representing the speed of the rotor on the one hand and the speed of the generator shaft on the other. This motor-driven transmission requires a large amount of control energy to consume at least 10 to 15% of the energy produced by the generator.

In recent implementations, in particular in the above mentioned schemes, the produced current can be used in a local grid, for example a group of houses. However, connecting these wind turbines to the national grid is still difficult or impossible.

It is an object of the present invention to address at least some of the above mentioned disadvantages in terms of reducing cost and / or complexity and / or improving energy efficiency and / or frequency stabilization in power production.

According to the invention there is provided a transmission for a machine that generates power from a power source, in particular a wind turbine rotor, of which the rotational speed is variable, comprising: a supporting structure, an input shaft connected to the power source, of the machine A transmission having an output shaft connected to the rotor and at least two shifting paths, the at least one shifting path passing through a differential mechanism having at least three rotary members In one of the shift paths is a dynamic coupling and kinematic uncoupling relationship, each of which has a relative speed relative to each other because it is connected to different parts of the transmission. Two rotary elements, said relative velocity being equal to between the two rotary elements It is characterized in that it is configured to cause relative rotation in a regulating apparatus that generates a torque which changes in a direction of maintaining the rotor of the system at a set speed, in particular at a substantially constant speed.

According to an embodiment of the invention, such a change in torque is defined by the characteristic relationship of the apparatus between that torque and the rotational speed in the apparatus. Optionally, the change in torque is determined by a control, in particular a control loop which regulates the speed of the rotor of the machine.

The change in torque applied by the regulating device between the two rotating elements makes it possible to influence the speed ratio set by the differential mechanism in a simple manner, and consequently the input and output shafts of the transmission. It is possible to influence the speed ratio between them.

After all, even if the rotational speed of the power source is extremely low, for example close to one revolution per minute, if desired, the transmission according to the invention can be set at the input of a power production machine that supplies power to the grid. In general, it makes it possible to maintain a constant speed.

Thus, for example, the transmission provides the possibility of keeping the power grid powered by the power generating machine constant, thereby periodically regulating the frequency of the current produced by the machine to match the frequency of the power grid. It is possible to prevent adjustments and thus eliminate the need to provide bulky, expensive equipment for this purpose.

The maximum output of the regulating device will be kept in an extremely limited state, for example on the order of 3 to 5% or less of the output of the main machine.

The regulating device may be a motor that injects additional mechanical energy into the transmission device to supplement the output shaft to drive the power production machine. If the regulating motor is an electric motor, power can be drawn by drawing power from the production from the power generating machine.

According to the invention, however, it is preferred that the regulating device is an electric generator. Such generators can supply power to many functional members of wind turbines or other types of power generation units. Such functional components may be, for example, a motor that directs the wind turbine's directing direction, a motor that directs the rotor's blades, a lighting or illuminated signaling devices, and the like. The excess power may be used to power the electric motor driving the output shaft of the transmission to increase the mechanical force supplied to the capacitor and / or the power production machine.

When control is possible, the generator or other regulating device can be controlled by a unique electrical signal that allows for extremely precise adjustment. The electrical signal may be generated after a permanent or periodic comparison of the rotational speed of the rotor of the production machine with a reference value for this speed. In addition, in generating the basic value of the signal, it is also possible to consider the rotational speed of the input shaft, and by changing the signal value according to this basic value, the rotor speed of the production machine is adjusted.

The regulating device may be an electric generator of a type capable of changing the number of electrodes. Such a generator can operate at an electrical speed that is different from the speed of movement between the rotor and the stator. This is because the layout of the transmission and the expected operating environment require a specification that adapts to a wide range of changes in the kinematic speed of the rotor relative to the stator in a regulating generator. The advantage is that efficiency and output can be optimized.

It is also possible to install the adjustment device directly between the two elements. In other words, in the adjusting device, there is a relative speed equal to the rotational speed difference of the two elements. For example, the rotor of an electric generator rotates with one of the elements, while in this case the other part, generally known as the stator, is an element that rotates with the other of the elements. In such a configuration, a rotary connection is required for the energy, typically the electrical energy coupling, of the regulating device, and also for the operation and regulation of the link which controls it and any other existent link. Moreover, in the general example of an electric generator, such an apparatus works satisfactorily only when the relative speed between the rotor and the stator is at least about 1000 revolutions per minute. This means that the regulating device has a predetermined power value.

The present invention proposes a useful solution which involves installing the apparatus directly between the two rotating elements described above. In this particular feature of the invention, the two elements described above represent a rotary output representing the difference between the absolute values of the rotational speeds of the two elements, possibly the weighted difference. Is connected to the two inputs of a comparative differential gearset having a), and the axis of the apparatus is connected to the rotary output.

In general, the apparatus is mounted between the rotational output and the support structure, and according to another useful characteristic structure, the device relates to the rotational speed of the rotational output of the comparative differential gearset. means for increasing the rotational speed of the axis of the apparatus.

Thus, the regulating device may have a fixed stator, and the absolute value of the speed of the rotor or other moving part is significantly reduced. Rotary coupling is no longer needed, and the input speed of the apparatus can be increased as much as possible with respect to the output speed of the comparative differential gearset, so that the lowest possible speed between the two rotating elements You can make a difference.

In one embodiment, the apparatus has means for causing the two rotating elements to rotate in opposite directions with respect to each other. In this case, the comparative differential gearset may be in the form of planetary pinions meshing with two sun gears facing each other. The planetary pinions are at the same speed as the algebraic mean of the speeds of the two sun gears, each of which constitutes one of the elements (and thus half of the difference in absolute values when the speeds are opposite to each other). It is held by a rotating cage.

As can be seen in the description of the specific embodiments below, there may also be a comparative differential gearset that can provide at the output a speed representing a difference between two rotational speeds, ie a weighted difference, in the same direction.

In the above, 'weighted difference' means a calculated difference between two values (two speed values) multiplied by other constants. Thus, for example, when the rotational speeds have the same absolute value, a non-zero weighted difference is obtained. This is useful in some embodiments described below, in particular in generating a speed proportional to the absolute value of the rotational speed of the two elements in the adjusting device.

More generally, the present invention provides a kinematic interruption between two mechanically continuous elements along a shift path, the difference between the absolute value of the velocities of the two elements by the rotary output, That is to say connecting these two elements to the two inputs of a comparative differential gearset designed to rotate at speeds that appear as weighted differences, the rotational output to an electric generator, a pump or the like or an energy injector such as a motor. It is taught to connect to a dynamic regulating energy tapping apparatus, which is characterized by the rotational speed of the shift path, the shift path through inherent inherent characteristics or control combined with this characteristic. Adjust the torque transmitted, the slip between the rotational speeds of the two elements and the like Set it.

Optionally, the shift path with the two elements comprises means for increasing the rotational speed of each element. The two elements thus rotate faster, and the given speed difference between the two elements corresponds to the lower power of the regulating device and the lower portion of the power passing through the shift path.

In a simple embodiment, one of the elements is in a fixed relationship with one of the input and output axes, and the other is in a fixed relationship with the rotation member of the differential mechanism, and the rotation The member itself is in engagement with each of the input and output axes in variable proportions.

In a preferred embodiment, at least one of said differential mechanisms has two differential mechanisms having three rotating members, said at least two shifting paths corresponding to one of said differential mechanisms rotating member of another mechanism. It has three shifting paths, each connecting to a rotating member.

The two elements typically form part of one of the three pathways.

This embodiment makes it possible to ensure that the two elements always rotate at speeds where the absolute values are substantially close to each other, although they are not identical, so that the transmission ratio between the input and output axes of the transmission is very wide. Even if it is changed from, the energy contained in the control device can be made very small and theoretically small as desired.

Optionally, one of the three shifting paths is an input path having a shifting member engaged to the input shaft and the other of the three shifting paths has a shifting member engaged to the output shaft. Output path. Thus, it is contemplated that the transmission has two differential mechanisms mounted in parallel between the input shaft and the output shaft and coupled to each other by a third shift path.

The device may be configured such that the difference between the two differential mechanisms and / or the difference in at least one of the transmission paths and / or the control device is such that the operating mechanism of the transmission device depends on the dynamical action of the adjustment device. There is a difference in the combination of the two rotating elements.

In one embodiment, this is suitable when the energy production machine must be set at a constant speed and thus the transmission ratio is a direct function of the speed of the input shaft, and the rotational speed applied to the apparatus by the two elements is Changes as a function of speed of the input axis. Therefore, the rotational speed of the apparatus determines the speed ratio.

In this example, when the drive torque applied to the input shaft is a power source consisting of a rotor of a wind turbine that gradually increases with the rotational speed of the input shaft, the force applied to the apparatus is increased when the speed of the input shaft increases. It is useful for increasing the rotation speed. Thus, when the apparatus, such as an electric generator, itself has a torque characteristic that increases with rotational speed, the increase in torque of the electric generator is accompanied by an increase in torque in the shift path comprising the two elements. . The assembly may be self-regulating. For example, by changing the excitation applied to the regulating device made of the electric generator, fine adjustment is possible.

One of the differential mechanisms is to generate two rotating members respectively connected to the input and output shafts, and to generate an average of the speed of the input shaft and the speed of the output shaft, possibly a weighted mean. It can be mounted in such a way as to have a third rotating member. In particular, when obtained as a function of the speed of the input axis, the obtained average applied at least indirectly to the third rotating member of another differential mechanism causes the other differential mechanism to produce the desired transmission ratio between the input axis and the output axis. ) Is selected. In this assembly, as mentioned above, one of the shift paths has a kinematic interruption which is connected by the dynamic coupling provided by the regulating device.

Optionally, the two differential mechanisms described above are identical to each other. In a first version, at least one of the three shifting paths is separated by the other one of the three shifting paths between the two rotating members to which the one shifting path connects. A speed ratio different from the speed ratio set between the two rotation members connected by the other speed change path is set.

Optionally, the mechanisms are identical to each other and two of the three shift paths set the same speed ratio, in particular the rotational member of one of the differential mechanisms and the rotational member of the other differential mechanism are cavities. This creates rigid connections that each ensure common rotation.

The third path connecting the two third rotating members of the two differential mechanisms to each other may have different mechanical transmission ratios to produce a difference in speed between the two rotating members.

In the second version, the two differential mechanisms described above have the same design but different tooth ratios. The three shift paths preferably set the same shift ratio.

Preferably, the two mechanisms are coaxially aligned, and at least one, preferably two, of the transmission paths ensure joint rotation of two rotating members each belonging to one of the mechanisms. Connections.

In particular, in equipment such as wind turbines where a high step-up ratio of the output shaft speed to a speed of the input shaft and a wide range of these ratios are required, the differential mechanism is a solar gear connected to the output shaft. And a planetary carrier connected to the input shaft and supporting at least one set of two planetary pinions mounted in the cascade, the ring gear consisting of a rotary reaction member. Made in the form of a main cyclic gearset, one of the two planetary pinions engages the sun gear and the other engages the ring gear. This type of differential mechanism varies from one to infinity as the speed of the ring gear changes from a speed equal to the speed of the sun gear to a speed equal to a fraction of the speed of the sun gear, respectively. It is noteworthy that it provides a step-up ratio. The fraction is equal to the tooth ratio between the sun gear and the ring gear. This is very useful in that it makes it possible to select a differential mechanism in which the number of teeth of the ring gear is twice the number of teeth of the sun gear.

A second subject of the invention is a unit comprising a transmission and a synchronous power generating machine according to the first subject mentioned above for producing electric power. The present invention makes the speed of the above-described power generating machine substantially completely stable, thereby allowing the machine to supply a stable current in terms of frequency and phase.

Optionally, the power generation unit controls the apparatus as a function of a sensor for detecting the rotational speed of the rotor of the power production machine and as a function of the difference between the rotational speed of the rotor and a setpoint. And a control loop for adjusting the rotation speed.

A third subject of the invention is a wind turbine having a transmission according to the first subject mentioned above and / or a power production unit according to the second subject mentioned above.

According to another aspect of the present invention, a method of setting a speed ratio between a power source and a load includes two differential mechanisms positioned between the power source and the load, each of which has at least three rotating members, Each rotating member of one of the mechanisms is connected to a separate rotating member of another mechanism by a separate shifting path, one of the paths having two rotating elements connected by the action of a kinetic apparatus and , The coupling device (apparatus) is characterized in that it is adjusted.

Other features and advantages of the present invention will be apparent from the following detailed description, but are not limited by the examples.
1 is an axial sectional view showing a first embodiment of a wind turbine according to the present invention;
FIG. 2 is a front view schematically showing an epicyclic gearset used in the wind turbine shown in FIG. 1,
3 is a half front view showing some of the features in dimensional and geometrical features and operation of the main power gear set described above;
4 to 10 are similar to FIG. 1 and show configurations related to other embodiments.
11 and 12 illustrate two different forms of comparative differential.
Hatching drawn on the rotating elements indicates the direction in which the rotating elements rotate. In the case of planetary pinions, they rotate about their own axis.

In the embodiment shown in FIG. 1, only a partially shown wind turbine is shown in the power generation machine 3 via an input step up gearing 4 which is connected to a transmission 6 according to the invention. A wind turbine rotor 1 for driving the rotor 2 is provided. The stator 7 of the machine 3 is fixed to the support structure 8 shown only symbolically. According to a preferred embodiment of the present invention, the power production machine 3 may be a synchronous generator which produces a completely stable speed, for example, 1500 revolutions per minute to stably produce 50 hertz currents suitable for the power grid. . The wind turbine rotor 1 rotates at a high variable speed, generally in the range of 1 to 30 revolutions per minute, depending on the strength of the wind. The up gear 4 increases this speed by a constant factor, for example 50 times. Thus, the output shaft of the upward gear portion 4, which also constitutes the input shaft 11 of the transmission 6 at the same time, is rotated at a speed in the range between 50 and 1500 revolutions per minute in this embodiment. The transmission 6 continuously raises the rotational speed of the output shaft 12 bound to the rotor 2 of the machine 3 with respect to the rotational speed of its input shaft 11 by 30 to 1 times. The speed ratio will be set.

The transmission 6 comprises a differential mechanism 13, in this embodiment three rotating members, ie a sun gear 14 connected to the output shaft 12, and a ring gear 16 which forms a reaction rotating member. And a planetary or epicyclic gearset consisting of a planet carrier 17 connected to the input shaft 11. The planet carrier 17 carries at least one set of two planet pinions 18, 19 engaged with each other while mounted in a cascade. The planetary pinion 18 meshes with the outer tooth set of the sun gear 14, and the planetary pinion 19 meshes with the inner tooth set of the ring gear 16.

This type of main power gearset with planetary pinion pairs in the cascade has the following characteristics: if the speed ratio between the input shaft 11 and the output shaft 12 is 1: 1, the sun gear 14, The ring gear 16 and the planet carrier 17 rotate at the same speed. When the speed ratio is 30: 1 (the rotation speed of the output shaft 30 is 30 times the rotation speed of the input shaft 11), the ring gear 16 is the input shaft 11 and the output shaft 12 In the same direction as the above, the rotation speed of the sun gear 14 is rotated at a speed close to the value multiplied by the ratio of R1 / R2. Where R1 is the tooth set radius of the sun gear and R2 is the tooth set radius of the ring gear 16 (see FIG. 3). In other words, in particular, if 1/2, which is reasonably reasonable as the ratio of R1 / R2, was selected, the rotational speed of the ring gear 16 would always be in the same direction, and the input speed Ve would change by 30 times and total When the transmission ratio is Vs / Ve, it may change only up to twice. The reaction torque CR acting on the ring gear 16 needs to be directed in the direction opposite to the direction of rotation SR of the input shaft 11. As shown in FIG. 3, the rotation performed by the planet carrier 17 between the position indicated by the dotted line and the position indicated by the solid line is indicated by α ₀ . When all three rotating members 14, 16, 17 rotate in the same direction, each of the sun gear 14 and the ring gear 16 are equal to the rotation α ₀ of the planet carrier 17, and α The rotation is increased by the angles indicated by ₁ and α ₂ . Since these two angles correspond to the arc length, there is a relationship of the ratio α ₂ / α ₁ = R 1 / R ₂ .

Therefore, the speed ratio is _equal to (α ₀ + α ₁ ) / α ₀ . The angle α ₀ represents the input speed Ve at which the input shaft 11 represents, and (α ₀ + α ₁ ) represents the output speed Vs set at 1500 revolutions per minute. From the foregoing, the speed Vc of the ring gear 17 can be calculated as follows: Vc = Ve + (Vs-Ve) (R1 / R2).

The transmission according to the invention adjusts the rotational speed Vc of the ring gear 16 so that the output shaft 12 rotates to the desired value Vs and / or the ratio of Vs / Ve in accordance with the above connection relationship. It will have a desirable value.

In order to enable control of the rotational speed of the ring gear 16, the transmission device 6 according to the invention has two transmission paths TC, between the input shaft 11 and the output shaft 12. TD). The kinematic path TC comprises the differential mechanism 13 and an intermediate shaft 21 rigidly connecting the sun gear 14 to the output shaft 12. The dynamic path TD has kinematic disturbances connected by the differential mechanism 13 and a specific dynamic link between the ring gear 16 and the output shaft 12.

More specifically, the transmission path TD has two rotating elements 22, 23 which are in a power transmission relationship, on the one hand, at the same time are separated kinematically and have relative speeds that cause rotation about each other. In this particular embodiment, the first rotating element 22 rotates at a rate fixed to the rotational speed of the ring gear 16. For this purpose, the first rotating element 22 is engaged with a pinion 24 which meshes with the outer tooth set 22 of the ring gear 16. The second rotating element 23 rotates at a rate fixed to the speed of the output shaft 12. For this purpose, the second rotating element 23 is engaged with the pinion 27 which meshes with the gear wheel 28 which is engaged with the output shaft 12. The intermediate shaft 21 extends between the sun gear 14 and the gear wheel 28. Thus, since the gear wheel 28 rotates in the form of a body with the intermediate shaft 21 and meshes with the pinion 27 at a fixed ratio, the shift paths TC, TD are at one end of the differential mechanism. By 13, at the other end are connected to each other by the gear wheel 28. The two rotating elements 22, 23 are in common with a common geometric axis fixed at a distance from and parallel to the overall axis 31 of the output axis 12 and the input axis 11. It is mounted so as to rotate about a geometric axis 29, the entire axis 31 also being the axis of the differential mechanism 13 and the intermediate axis 21.

An adjusting device 32 is coupled between the rotating elements 22, 23 to set the torque which varies in the direction of holding the rotor 2 of the machine 3 at a set speed, in particular at a substantially constant speed. Done.

In the example shown, the regulating device 32 is an electric generator, for example an alternator, which is bound to the element 22 in which the rotor 33 rotates at a set speed relative to the ring gear 16. The stator 34 of the electric generator 32 is fixed like a normal stator, but instead of the second rotating element 23 and one body which rotates at a set speed with respect to the output shaft 12 in this embodiment. Rotating stator rotating in the form of.

Tooth ratio between the pinion 24 and the outer tooth set 26 of the ring gear 16 on the one hand, tooth tooth between the pinion 27 and the gear wheel 28 on the other hand ratio is as follows: i) the rotary elements 22, 23 rotate in the same direction, and ii) the rotational speed of the rotary element 22 coupled to the ring gear 16 is the output shaft 12. Is always greater than the rotational speed of the rotating element 23 coupled to

In the embodiment where R2 / R1 = 2, the minimum possible speed of the ring gear 16 is half the speed of the output shaft 12. Thus, by gradually increasing the rotational speed of the element 22 with respect to the ring gear 16 to about twice the rotational speed of the element 23 with respect to the output shaft 12, the first rotating element ( It can be ensured that 22) always rotates faster than the second rotating element 23.

In general, this step-up ratio is chosen to be relatively high such that the rotating elements 22, 23 rotate at a relatively higher speed compared to the speed of the input shaft 11 and the output shaft 12. do. For example, it is possible to design the second rotating element 23 to rotate at a speed of 14,000 revolutions per minute, and the first rotating element 22 to rotate at a speed between 15,000 and 30,000 revolutions per minute.

At all operating speeds, the rotor 33 rotates faster than the rotatable stator 34. Electromagnetic forces present between the rotor 33 and the stator 34 are in a direction of decelerating the rotor 33, and thus the ring gear 16, and the stator 34, and thus the output shaft. It acts in the direction of accelerating (12). Energy transfer therefore takes place from the differential mechanism 13 to the output shaft 12 along the dynamic shift path TD. This also means that the gear 14 receives the torque from the planetary pinion 18 from the input shaft 11 via the kinematic shift path TC because it receives the torque in the direction of rotation SR (Fig. 3) of the gear. Energy transfer is made to the shaft 12. Thus, in this embodiment, two shift paths drive the output shaft 12.

The torque transmitted through the dynamic shift path TD is proportional to the input torque on the input shaft 11. Since the speed Vs of the output shaft 12 is constant, the rotational speed of the rotor 33 with respect to the stator 34 is a function of only the rotational speed Ve of the input shaft 11. Moreover, in the special case of a power source such as a wind turbine, the torque on the input shaft 11 increases, for example, proportionally, with the rotational speed Ve of the input shaft 11. As a result, the adjustment according to the invention indicates that when the rotational speed of the rotor 33 with respect to the stator 34 is increased, the electromagnetic torque between the rotor 33 and the stator 34 is increased. Entails. By selecting the regulating device 32 having a properly selected characteristic curve in relation to the torque as a function of the rotational speed of the rotor relative to the stator, the rotor of the power production machine 3 without the need for regulating control circuitry A transmission device capable of automatically stabilizing the rotational speed of (2) is created.

However, in the illustrated embodiment, in view of achieving finer adjustment and better precision of the rotational speed of the rotor 2 of the power production machine 3, an adjustment device is provided. This includes a sensor 36 for detecting the rotational speed of the output shaft 12, a memory for storing a reference set value for the rotational speed of the rotor 2, or an element 37 corresponding thereto, and the output shaft 12. Excitation applied to the stator 34 via a comparator 38 and one or more rotary contacts 41 provided on the rotating element 23 to determine a possible difference between the actual speed and the setpoint A circuit 39 for converting the output from the comparator 38 into an excitation current. In the illustrated embodiment, as one of the improvements, a sensor 42 for detecting the rotational speed Ve of the input shaft 11 is provided. The sensor 42 sends a signal to the circuit 39 for selecting a range of excitation current values as a function of the speed Ve. When the rotational speed Vs of the output shaft 12 becomes insufficient, the excitation of the generator 32 increases to further decelerate the ring gear 16 and thus the input shaft 11 and the output shaft. Promotes a slight increase in the speed ratio between 12. On the contrary, if due to symmetry, the speed Vs is about to be excessive, the control and regulation circuit described above slightly reduces the above excitation in order to lower the speed ratio.

In a manner not shown, a device for continuously performing automatic speed conversion or one with a finite number of ratios is provided on the shift path TD, for example, It may be arranged between the pinion 24 and the stator 34. Automatic control of the device has the tendency to adjust the rotational speed of the rotor 33 at all times or periodically, thereby realizing an optimal difference to the rotational speed of the stator 34. This improves the efficiency of the regulating generator 32 and, in particular, by reducing the speed difference between the rotor 33 and the stator 34 in the state where the speed Ve of the input shaft 11 is high. The power absorbed by 32 can be significantly reduced. In principle, the aforementioned control circuit automatically corrects the excitation of the generator 32 as a function of the speed ratio made by the speed converter. It may also be possible to provide the circuit 39 with an input of a signal informing the circuit 39 of the ratio made by the speed converter. The circuit 39 can thus predict the variation of the excitation performed rather than reacting to the variation in the rotational speed of the rotor 2 of the machine 3. Furthermore, the presence of the speed converter is on the one hand between the ring gear 16 and the pinion 24, and on the other hand between the gear wheel 28 and the pinion 27, as mentioned above. It is possible to provide a ratio, which in any case is presented by way of example only.

Alternatively or in addition to the speed converter, the generator 32 may be manufactured in the form of an electrode change generator. This known type of generator performs variable electrical rotation of the rotor electrodes relative to the mechanical structure of the stator. In this way, it is possible to change, in particular optimize, the electrical speed difference between the rotor and the stator. To this end, the circuit 39 is supplied by the detector 42 and takes into account the signal indicative of the input speed Ve, via the rotary contact 41 or any other rotary contact that may be further provided. It is designed to convey the appropriate command to 34.

The power produced by the generator 32 is collected, for example, by rotary rotor contacts 43 provided on the outer circumferential surface of the rotary element 22. This electrical energy, for example, reaches rectifier 44 to charge capacitor 46 and / or to supply power to one or more terminals 47 for one or more power equipment.

In the following embodiments, the electrical control means or the energy collection means produced by the generator 32 are not shown and the detailed description thereof will be omitted. This means, at least in theory, that it is similar to that described above and disclosed with reference to FIG. 1.

The embodiment shown in FIG. 4 will be described only with respect to other parts compared to the embodiment shown in FIGS. 1 to 3.

Instead of having a fixed speed ratio relationship with the output shaft 12, the second rotating element 23 is now in a fixed speed ratio relationship with the cage 48 of the third rotating element or the second differential mechanism 49. have. The two first rotating members of the second differential mechanism 49 are two bevel sun gears 51, 52 which face each other while having the same tooth set. One of these two sun gears is in fixed speed ratio relationship with the input shaft 11 and the other with the output shaft 12. These three rotating members 48, 51, 52 are mounted with respect to the stationary structure and the rotating shaft 29 of the rotating elements 22, 23 and the rotating shaft of the input / output shafts 11, 12 ( 31 have a common axis of rotation 53, spaced apart from each other.

Bevel planet pinions 54 are mounted in the cage 48 that rotate freely about an axis perpendicular to the axis 53. Each bevel planetary pinion 54 meshes with the two sun gears 51, 52. In this differential mechanism, the cage 48 rotates about the common axis 53 at a speed equal to the algebraic mean of the rotational speeds of the two sun gears. In this case, the two sun gears are set to rotate in the same direction. Thus, the cage 48 is rotated at a speed represented by an arithmetic mean of the speeds of the input / output shafts 11, 12.

In this embodiment, the two rotating members 16, 48, connected via a third path, have a tendency to reduce the transmission ratio of their differential mechanism when one of them 16 increases in speed. One 48 is inclined to increase the transmission ratio of the differential mechanism when its speed is increased.

The principle underlying this embodiment is as follows: When the speed Ve of the input shaft 11 varies from 50 revolutions per minute to 1500 revolutions, the speed of the ring gear 16 is approximately from 750 revolutions to 1500 revolutions per minute. It is necessary to change, as is the change in the average of the speed of the input shaft and the speed of the output shaft. This idea is to generate the speed represented by this average value and apply it directly or indirectly to the ring gear 16. In the illustrated embodiment, the adjustment device 32 is arranged between the cage 48 and the ring gear 16 and the torque acting in the opposite direction of the rotational direction is applied to the ring gear 16 in the input embodiment. And the speed produced from the output speeds, with the speed changing in a manner similar to the speed desired for the ring gear but still being lower than this speed. Applies to the stator of (32). Thus, there is always a very small speed difference between the stator and the rotor of the generator 32, representing a small portion of the speed of the elements 22, 23, so that the generator ( The power absorbed by 32 is lowered.

Common regulating devices, such as electric generators, need to have a rotor speed of at least a constant level, for example at least 1000 revolutions per minute, compared to the stator speed in order to function properly. For this speed difference representing a small part of the speed of the rotating elements 22, 23, the speed of the rotating elements 22, 23 relative to the speed of the input shaft 11 and the output shaft 12 is gradually increased. It is desirable to provide a means for raising.

In the illustrated embodiment, for example, the pinion 24 bound to the rotary element 22 has a diameter equal to 1/20 of the outer tooth set diameter of the ring gear 16. The element 22 thus rotates 20 times faster than the ring gear 16. In addition, lift gear sets 56, 57 are provided between the input shaft 11 and the sun gear 51 on the one hand and between the output shaft 12 and the sun gear 52 on the other hand. do. Therefore, the rotational speed of the cage 48 has an amplified value with respect to the arithmetic mean value of the veins Ve and Vs. This amplified mean value is transmitted to the rotating element 23 at a ratio of 1: 1.

It is also suitable for the average speed supplied by the cage 48 to correspond to a weighted average. Thus, the relationship between the rotational speed of the cage 48 on the one hand and the ratio of Ve / Vs on the other hand can be finely adjusted.

This is more readily understood when considering a numerical example based on the above mentioned values. The ring gear 16 rotates at a speed of 750 revolutions per minute to 1500 revolutions per minute. The element 22 rotates at a speed 20 times faster, say 15,000 revolutions per minute to 30,000 revolutions. If it is desired that the speed difference between the elements 22 and 23 be between 1,000 revolutions per minute and 2,000 revolutions per minute, then the element 22, and further the cage 48, must rotate at a speed of 14,000 revolutions per minute to 28,000 revolutions. This is achieved (usually) when the ascent rate of the gearset 56 is 19: 1 and the ascent rate of the gearset 57 is 18: 1. In this setting, the energy absorbed by the generator 32 is on the order of 6-7% of the energy flowing along the shift path T3.

In the embodiment shown in FIG. 4, three geometric axes 29, 31, 53 are shown on the same plane. This is not an absolute key; At the same time maintaining the desired ratio, the gearsets 56, 57 may change the diameter appropriately so that the elements above the line 55 may change direction from the plane on the drawing.

The underlying principle of the current version of the invention and the versions to be described below can be implemented in different ways: Two differential mechanisms 13, 48 are parallel between the input axis 11 and the output axis 12. Is fitted. Each differential mechanism has input members 17 and 51 connected to the input shaft 11, output members 14 and 52 connected to the output shaft 12 and reaction members 16 and 48. The two reaction members 16, 48 are connected to each other via the transmission path T3 but are not in a fixed proportional relationship with the input shaft 11 or the output shaft 12. In the section connecting the rotational elements of the two mechanisms there is a kinematic disturbance connected by a dynamic coupling (generator 32).

Energy can be connected from the transmission via this dynamic coupling. It is also possible to replace the generator with a motor powered by the machine 3, which will inject a variable amount of energy into the transmission. Energetic activation of the dynamic coupling is the result of rational selection of all tooth ratios in the transmission. This choice means that each differential mechanism is subjected to a level of stress set directly or indirectly by dynamic coupling from the other differential mechanism.

In the embodiment shown in FIG. 4, the two differential mechanisms described above will be in a relationship other than the one corresponding to the elements 22, 23 in which the speeds of their reaction members 16, 48 are bound to each other. Only when the speed ratio between the input shaft 11 and the output shaft 12 can be set equal. Since the speed ratio between the input shaft 11 and the output shaft 12 must be set equally, there is a speed difference between the elements 22, 23 as a function of the Vs / Ve ratio. Thus, the speed ratio Vs / Ve can be set by adjusting the speed difference between the elements 22 and 23. This difference in speed is controlled by controlling the activation of the kinetic bond 32.

There is a third way to describe the embodiment shown in FIG. 4, which will be described below. Two differential mechanisms 13 and 49 are connected via three shift paths. The first path T1 or the input path has a set tooth ratio, and the input shaft 11 of the input member 17 and the second mechanism 49 of the first mechanism 13 is turned on. The input member 51 is connected. The second path T2 or the output path has the set tooth ratio and outputs the output shaft 12 to the output member 14 of the first mechanism 13 and to the output of the second mechanism 49. The member 52 is connected. The third path T3 or reaction path connects the reaction member 16 of the first mechanism 13 to the reaction member 48 of the second mechanism 49 at a set tooth ratio. do. In one of the three pathways there is a kinematic disorder linked by kinetic coupling. Furthermore, in the above-mentioned differential mechanisms and / or in the tooth ratio of the three paths and / or in connection of the rotating elements 22, 23 to the regulating device, the regulating device has a total transmission ratio Ve /. It is characterized in that it is activated differently according to Vs and / or depending on the input speed Ve and / or the torque transmitted. The characteristic curve of the regulating device and / or the control of the regulating device enable the entire transmission ratio Ve / Vs to be controlled.

The embodiment shown in FIG. 5 will be described only with respect to other points compared to the embodiment shown in FIG. 4.

In this embodiment, the dynamic coupling by the adjusting device 32 is not disposed in the third shift path T3 between the ring gear 16 and the cage 48, and the second shift path or output path is not present. It is disposed at T2. More specifically, the kinematic disturbances connected by the dynamic coupling 32 are on the one hand an output member 52 of the second differential mechanism 49 and a lift gear part connected to the output shaft 12. step up gearing). The third shift path T3 is greatly simplified because it is configured to engage directly between the outer circumferential surface of the ring gear 16 and the cage 48. Here, there are now only two geometric axes, the entire axis 31 and an axis 53 common to the differential mechanism 49 and the generator 32. There is one less intermediate pinion in the lift gear sets 56, 57.

The embodiment shown in FIG. 6 will be described only with respect to other points in relation to the embodiment shown in FIG. 5.

In this embodiment, the differential mechanism 13 has a form with simple planetary pinions 58 rather than a pair of planetary pinions in the cascade. Each planetary pinion 58 meshes with the inner tooth set of the sun gear 14 and the ring gear 16.

This differential mechanism provides a high rate of rise of the sun gear 14 relative to the planet carrier 17 when the ring gear 16 rotates in a direction opposite to the planet carrier 17 and the sun gear 14. to provide. Optionally, for example, when the inner gear set diameter of the ring gear 16 is three times the diameter of the sun gear 14, the ascent rate reaches 3: 1 when the ring gear is kept stationary, When the ring gear rotates 43.5 times faster than the input shaft 11, the ascent rate reaches 90: 1.

In this case, the lift gear portion 4 only generates a rise ratio of approximately 17: 1, which means that the rotational speed of the input shaft 11 now varies from 17 revolutions per minute to 500 revolutions. When the speed of the input shaft 11 is 17 revolutions per minute, the transmission must provide its maximum rate of climb. This causes the ring gear 16 to run at maximum speed, 17 x 43.5 = 740 revolutions per minute, which is very reasonable.

It is therefore important to vary the rotational speed of the ring gear 16 from -740 revolutions per minute to zero revolutions. This causes the cage 48 to generate i) an average of the speed of one of the input / output shafts 11, 12 and ii) the inverse speed of the other of the shafts 11, 12. This can be achieved by. Thus, the gearset 57 has a reverse idler pinion 59, while the gearset 56 does not have an inverted idle pinion.

In addition, the rate of increase of the gear set 56 is approximately three times higher than the rate of increase of the gear set 57. When the input speed is very low, the speed of the cage 48 is close to half of the speed of the output shaft 12. Conversely, when the input speed is at its maximum value (500 revolutions per minute), the average value supplied by the cage 48 toward the differential mechanism 49 is increased by three times the output shaft speed. It is introduced in the opposite direction to have a phosphorus effect. Accordingly, the speed of the cage 48 is changed in a desired manner with respect to the speed of the input shaft 11. It is transmitted to the ring gear 16 in the proper direction so that the latter rotates in the opposite direction to the input shaft 11 and the output shaft 12.

In this embodiment, the torque applied to the ring gear 16 needs to be the same as the direction of rotation thereof. For this reason, the generator 32 must be driven in conjunction with the ring gear 16 rather than merely mechanically resisting it. Thus, the mounting of the generator must be in reverse when compared to the embodiments illustrated above, whereby the rotatable stator 34 is on the same side as the ring gear 16 and the rotor 33 is at the reference speed, In other words, it is a fixed ratio with respect to one of the input / output shafts, and in this embodiment is on the same side as the output shaft 12.

Of course, as in the preceding embodiment, the rate of ascent between the gearsets 56 and 57 and the ring gear 16 and the cage 48 is determined by the adjustment device 32 between the stator and the rotor. Carefully chosen to optimize for relative speed.

The embodiment shown in FIG. 7, like the embodiment shown in FIG. 6, is another modification of the embodiment shown in FIG. 5 and will only be described with respect to the other points with respect to the embodiment shown in FIG. 5.

The kinematic disorder with kinematic coupling by the regulating device 32 is now again positioned in the second shift path or output path T2, the sun gear 14 of the first differential mechanism 13. And gear wheel 28. In other words, the intermediate shaft 21 is interrupted. On the one hand the rotor 33 and on the other hand the stator 34 are respectively coupled to the sun gear 14 and the gear wheel 28 via lift gear sets 61, 63, 62, 28. . The tooth ratios are selected such that, for example, one of the rotating elements 22, 23 coupled to the sun gear 14 rotates faster than the other.

The embodiment shown in FIG. 8 will only be described with respect to other points in relation to the embodiment shown in FIG. 7.

In this embodiment, the two differential mechanisms are coaxially aligned along the entire axis 31. The input shift path T1 is a rigid coupling between the input shaft 11 and the planet carrier 17 and the input sun gear 51 of the mechanism 49. The third shift path T3 is a bell housing 64 that tightly connects the ring gear 13 and the cage 48. The sun gear 14, the intermediate shaft 21 and the gear wheel 63 forming the tubular assembly freely rotate about the input shaft 11. The gear wheel 63 is on the sun gear 14 side on the wind turbine rotor 1. The two differential mechanisms 13, 49 are located at intervals between the gear wheels 63, 28.

This embodiment operates similarly to one of the preceding embodiments. This requires fewer gearsets. However, a torque, such as the first differential mechanism 13, is generally applied to the second differential mechanism 49 rather than a torque reduced by step up gearing as in the case of the preceding embodiments.

The embodiment shown in FIG. 9 will be described only with respect to other points in relation to the embodiment shown in FIG. 8.

The first differential mechanisms are for the differential mechanisms 13, 113 having the same design and the same tooth ratio as shown in FIG. 1. Preferably, these two mechanisms have identical components for ease of manufacture, cost savings and parts inventory. The first shift path T1 tightly connects the input shaft 11 to the two planet carriers 17 and 117. The second shift path T2 connects the two sun gears 14, 114 tightly to the output shaft 12. The third shift path T3 connects the two ring gears 16, 116 through a kinematic obstacle which is connected by a kinetic coupling which will be described below.

The two ring mechanisms 16, 116 are rotated as if the two differential mechanisms are identical to each other and the sun gears 14, 114 are one body, as do the planet carriers 17, 117. It will also rotate in the same direction at the same speed. However, because they are coupled to the ring gear 16 and the ring gear 116, respectively, by the gearsets 66, 166 with slightly different ratios, the rotating elements 22, 23 have different rotational speeds. Will have The speed difference of the elements 22, 23 is proportional to the speed of the ring gears 16, 116, and the speed itself of the ring gears 16, 116 is dependent on the transmission ratio Vs / Ve. The dynamic action by the regulating device 32 can affect the speed difference between the elements 22, 23, and consequently the overall speed ratio.

Other differential mechanisms independent of the first differential mechanisms described above relate to the dynamic coupling mode between the elements 22, 23. The rotor 133 and the stator 134 are no longer directly connected to the elements 22, 23, but are installed between the elements 22, 23 so that the elements 22, 23 between them. And means for generating a speed indicative of the speed difference. The differential mechanism 141 in a conventional configuration performs the function on the assumption that the axes 22, 23 rotate in opposite directions. This is because the lift gearset 166 has a reverse idler pinion which is not provided in the lift gearset 66. Each of the elements 22, 23 is connected to each of the two input sun gears 143 of the comparison differential mechanism 141. These two bevel sun gears 141, which are arranged symmetrically facing each other, are freely rotatable on one or more axes perpendicular to the elements 22, 23 in the rotation cage 146. Engage with bevel planetary pinions 144. In operation, the cage rotates at a speed equal to half the difference between the absolute values of the speeds of the elements 22, 23. The cage 146 has, on its outer circumferential surface, a ring gear 147 that engages with the rising pinion 148 that is coupled to the rotor 133 of the adjusting device 32. The stator 134 of the apparatus 32 is mounted to a support structure.

Dynamic coupling in this manner is particularly useful because the speed of the rotor is significantly reduced and the stator of the regulating device remains fixed. This makes construction and placement much easier and no longer requires rotating contacts installed on the stator.

Moreover, in the preceding embodiments with the rotatable stator, a minimum speed difference between the elements 22, 23 was required for proper operation of the regulating device. At maximum speeds of up to 30,000 revolutions per minute that should not be exceeded in order not to rely on special and expensive components, the percentage energy contained in the regulating device is at least as large as the energy delivered by the dynamic coupling. 5%. With the structure shown in FIG. 9, the speed difference between the elements 22, 23 can be further lowered. As the speed difference is lowered, the rate of rise of the pinion 148 relative to the cage 146 may be further increased in all cases where a range of speeds suitable for the rotor 133 are desired.

The embodiment shown in FIG. 10 will be described only with respect to other points in relation to the embodiment shown in FIG. 9. In the present embodiment, the two ring gears 16 and 116 are tightly connected to each other. On the other hand, the output shift path T2 connecting the two sun gears 14, 114 has a kinematic disturbance connected by the same kind of dynamic coupling as disclosed through FIG. 9.

If the two differential mechanisms are the same as in FIG. 9, the speed difference between the rotating elements 22, 23 will be constant because it is proportional to the rotational speed of the output shaft 12. Nevertheless, the torque of the generator 32 may be set to adjust the speed ratio. In other words, adjusting the rotational speed of the output shaft 12 simultaneously adjusts the rotational speed of the rotor of the generator 32.

In the example shown, as mentioned in the preceding paragraph, a difference in speed between the elements 22, 23 is provided which is not constant and which changes as a function of the speed of the input axis 11. To this end, two differential mechanisms of the same design but somewhat different tooth ratios are used. Nevertheless, the difference in ascent rate between the lift gearsets 66 and 166 is maintained. Thus, when the transmission operates in direct drive so that the two sun gears 14, 114 rotate at the same speed, a difference in speed occurs between the elements 22, 23.

In an embodiment not shown, this embodiment may be implemented via two differential mechanisms of the same type as the one 13 shown in FIG. 6, namely a simple planetary pinion and a ring gear rotating in opposite directions. The operation of rotating the ring gear in one direction or another can also be considered. A gear ratio of 30: 1 (when the ring gear rotates at the speed of approximately 13.5 times the output speed in the opposite direction) and a gear ratio of 1: 1 (the ring gear rotates at the same speed and in the same direction as the input shaft) It is also possible to actuate a differential mechanism with the simple planetary pinions shown in FIG.

11 and 12 differ in terms of comparative differential mechanisms.

In the embodiment shown in FIG. 11, the two sun gears 143 have different diameters, and the planetary pinions 144 have inclined axes. When the elements 22, 23 have the same speed, the cage 41 rotates at a speed proportional to the speed of the elements 22, 23. With reference to FIG. 9, it is no longer necessary to provide another ratio for the step up mechanisms 66, 166. It is sufficient that one of them has a reversing facility and the other does not.

In the embodiment shown in FIG. 12, it is no longer necessary for one of the step-up devices to have an opposite installation. The inversion operation is done through a differential mechanism. Each planetary pinion 144 has coaxial tooth sets that engage the teeth of the sun gears 143. The two sun gears 143 are located together on one side of the planetary pinion axes. By differently selecting tooth ratios of the respective sun gears 143 together with the planetary pinion tooth sets, the elements 22 and 23 also rotate when the elements 22 and 23 rotate at the same speed. Rotation may also be made proportional to the speed of the elements 22, 23. This embodiment makes it possible to fabricate the two lifting devices 66, 166 exactly identically, although the two differential mechanisms are also identical.

Of course, the present invention is not limited to the above-described or illustrated embodiments. The kinetic coupling system with the comparative differential mechanism can also be implemented through other embodiments, in particular the embodiments shown in FIGS. 4 to 8. The comparative differential mechanism may not be cage type. For example, with the other rotating element connected to the sun gear of the epicyclic gearset, one of the rotating elements can be connected to the ring gear of a conventional main power gearset, the two rotating elements being mutually It is rotated in the opposite direction and is driven by lifting devices having a transmission ratio that slows down the planet carrier, for example by causing the ring gear to rotate about half the sun gear speed.

In the embodiment shown in FIG. 1, the kinematic path TC and the kinematic path TD may be installed between the input shaft 11 and the differential mechanism 13.

In embodiments as shown through FIGS. 4 to 12, the kinematic disturbances connected by the kinetic coupling are the input shift between the input shaft 11 and the rotational input member of one of the two differential mechanisms. It can be located in the path.

In most embodiments, the speed difference between the two rotating elements 22, 23 increases as the speed of the input shaft increases and the speed ratio decreases. Since the regulating device 32 is also generally characterized in that its torque increases as a function of speed, the speed difference between the two rotating elements in the example of a wind turbine with an increase in input speed accompanied by an increase in transmission torque. The direction of change contributes to the adjustment of the transmission. However, it is also conceivable not to change the speed difference or to change in the opposite direction as described above.

Claims (31)

As a transmission for a power source 1 having a variable rotational speed, in particular a machine 3 for generating power from a wind turbine rotor, a support structure 8, an input shaft connected to the power source 11, an output shaft 12 connected to the rotor 2 of the machine and at least two shift paths TC, TD; T1, T2, T3, wherein at least one shift path Passes through at least one differential mechanism 13, 49, 113 with at least three rotary members 14, 16, 17; 48, 51, 52; 114, 116, 117. In a shifting device, one of the shifting paths is a dynamic coupling and kinematic uncoupling relationship, each of which is relative to each other by being connected to different parts of the transmission. Two rotary elements 22, 23 with velocity And said relative speed is adjusted to generate a torque which varies between two rotating elements 22, 23 in a direction that maintains the machine's rotor 2 at a set speed, in particular at a substantially constant speed. A shifting device, characterized in that it is arranged to cause relative rotation in a regulating apparatus (32).
A transmission according to claim 1, wherein the change in torque is set by the characteristic relationship of the apparatus (32) between the torque and the rotational speed in the apparatus.
2. Transmission according to claim 1, characterized in that the change in torque is set by a control for adjusting the speed of the rotor (2) of the machine (3), in particular a control loop (36, 37, 38, 39). .
A transmission according to any one of the preceding claims, characterized in that the apparatus (32) is an electric generator.
5. The shifting device according to claim 4, wherein the electric generator (32) is an electric generator of a type capable of changing the number of electrodes.
6. The method according to any one of the preceding claims, wherein the two elements (22, 23) are the difference between the absolute values of the rotational speeds of the two elements, possibly the weighted difference. Connected to two inputs of a comparative differential gearset 141 having a rotary output 146 representing the rotational portion 133 of the device. Transmission device, characterized in that connected to the output (146).
7. Transmission according to claim 6, characterized in that the apparatus (32) is functionally mounted between the rotary output (141) and the support structure (8).
8. A means according to claim 6 or 7, wherein the rotational speed of the rotational portion 133 of the apparatus 32 is increased relative to the rotational speed of the rotational output portion 146 of the comparative differential gearset 141. And (147, 148).
10. Transmission according to any one of claims 6 to 8, characterized in that it comprises means (116) for rotating the two rotating elements (22, 23) in opposite directions with respect to each other.
10. The transmission path according to any one of the preceding claims, wherein the shift path with the two elements (22, 23) comprises means (24, 27; 56, 57; 61) for increasing the rotational speed of each element. 62, 66, 166.
11. A method according to any of the preceding claims, wherein one of the elements (23) is in engagement with one of the input and output axes (12) at a fixed rate and the other (22) The rotation mechanism 16 is engaged with the rotating member 16 of the differential mechanism 13 at a fixed ratio, and the rotation member 16 itself is engaged with the input and output shafts 11 and 12 at a variable ratio. Characterized in that the transmission.
12. The method according to any one of the preceding claims, wherein said at least one differential mechanism comprises two differential mechanisms (13, 49; 113) with three rotating members, said at least two shifts The paths are characterized in that they comprise three shifting paths (T1, T2, T3) each connecting one rotating member of said differential mechanisms to a corresponding rotating member of the other mechanism.
13. Transmission according to claim 12, characterized in that the two elements (22, 23) form part of one of the three paths.
14. An input path T1 according to claim 12 or 13, wherein one of said three shift paths is an input path T1 having a shift member 17 bound to said input shaft 11, wherein said three shift paths. The other of which is an output path (T2) having a transmission member (21, 28) coupled to the output shaft (12).
The two rotating members connected via the third path T3 have a propensity to reduce the transmission ratio of the differential mechanism when one of them 16 is increased. 48 is characterized in that the propensity to increase the speed ratio of the differential mechanism is increased when its speed is increased.
14. The rotational speed according to claim 12 or 13, when the speed of the input shaft 11 is increased, the rotational speed applied to the apparatus 32 by the two elements 22, 23 is increased. Transmission characterized in that it changes as a function of the speed of the input shaft (11).
17. Transmission according to claim 16, characterized in that the speed of rotation applied to the apparatus (32) is increased when the speed of the input shaft (11) is increased.
18. Approximate average of the opposite of the speed of one of the input / output shafts 11, 12 and the speed of the other of the input / output shafts 11, 12. In other words, in order to provide a weighted and / or amplified average to its third rotating member 48, the two rotating members 51, 52 of one of the differential mechanisms 49 are connected to the input shaft 11. And the third shift path T3 are speeds as a function of said weighted average and opposite directions of rotational speed of said input shaft 11 and output shaft 12. A speed change device characterized in that the phosphorus speed is applied to another third member (16) of said differential mechanism (13).
18. The method according to any one of claims 12 to 17, wherein the third rotation is the approximate average of the speed of the input shaft 11 and the speed of the output shaft 12, i.e. the weighted and / or amplified average. To provide to the member 48, two rotating members 51, 52 of one of the differential mechanisms 49 are connected to each of the input shaft 11 and the output shaft 12, and the third The transmission path of T3 is characterized in that the speed as a function of the weighted average is applied to the third member (16) of the other differential mechanism (13).
18. The method according to any one of claims 12 to 17, wherein the two differential mechanisms (13, 113) are identical to each other, and at least one of the three shift paths described above is connected by one of the shift paths. A speed ratio different from the speed ratio set between the two rotational members connected by the other one of the three shifting paths by another one of the three shifting paths. Device.
18. Transmission according to any one of claims 12 to 17, characterized in that the two differential mechanisms (13, 113) are identical to each other and two of the three shift paths set the same transmission ratio to each other. .
22. Transmission according to claim 21, characterized in that the three shifting paths set the same transmission ratio to each other, and the two elements (22, 23) are connected to the apparatus (32) differently.
18. A transmission according to any one of claims 12 to 17, wherein the two differential mechanisms are of the same design and have different tooth ratios.
24. The shifting device according to claim 23, wherein the three shifting paths set the same shift ratio.
25. The method according to any one of claims 16 to 24, wherein the two mechanisms (12, 113) are coaxially aligned and at least one of the shift paths, preferably two of the shift paths are among the mechanisms. A transmission, characterized in that the connections ensure that the two rotating members each belonging to one rotate jointly.
26. The input according to any one of the preceding claims, wherein the differential mechanism comprises a sun gear (14) connected to the output shaft (12), a ring gear (16) consisting of a rotary reaction member and the input. Epicyclic gear set having a planet carrier 17 connected to the shaft 11 and supporting at least one set of two planet pinions 18, 19 mounted in the cascade. It is made in the form of a gearset, characterized in that one of the two planetary pinions (18) is meshed with the sun gear (14) and the other is meshed with the ring gear (16). Transmission.
A unit for producing electric power, characterized in that it comprises a transmission (6) according to any one of claims 1 to 26 and a synchronous power production machine (3).
28. The apparatus according to claim 27, wherein the sensor 36 detects the rotational speed of the rotor 2 of the power production machine 3 and the device as a function of the difference between the rotational speed of the rotor and a setpoint. and a control loop for controlling the rotation speed by controlling the apparatus (32).
Wind turbine, characterized in that it comprises a transmission (6) according to any one of claims 1 to 26 and / or a power production unit according to claims 27 or 28.
In the method of setting the speed ratio between the power source 1 and the load 3, two differential mechanisms 13, 48 and 113 are located between the power source and the load, each of which is at least three different. Two rotating members, each rotating member of one of the mechanisms being connected to the individual rotating members of the other mechanism by means of individual shifting paths T1, T2, T3, one of the paths being a dynamic coupling device ( and two rotating elements (22, 23) connected by the action of the apparatus but not kinematically, said apparatus being regulated.
31. The output 146 of the comparative differential gearset 141 according to claim 30, wherein the dynamic coupling device 32 has two inputs each consisting of one of the elements 22, 23. And a shaft which is a driving relationship.

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